SG176259A1 - Rotating wheel used for direct-connection low-speed small-scale mixed-flow hydroturbine of hydrodynamic energy-saving cooling tower - Google Patents
Rotating wheel used for direct-connection low-speed small-scale mixed-flow hydroturbine of hydrodynamic energy-saving cooling tower Download PDFInfo
- Publication number
- SG176259A1 SG176259A1 SG2011087624A SG2011087624A SG176259A1 SG 176259 A1 SG176259 A1 SG 176259A1 SG 2011087624 A SG2011087624 A SG 2011087624A SG 2011087624 A SG2011087624 A SG 2011087624A SG 176259 A1 SG176259 A1 SG 176259A1
- Authority
- SG
- Singapore
- Prior art keywords
- water
- diameter
- rotational speed
- runner
- blades
- Prior art date
Links
- 238000001816 cooling Methods 0.000 title claims description 30
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 94
- 238000006243 chemical reaction Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 238000002474 experimental method Methods 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 239000002023 wood Substances 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000001228 spectrum Methods 0.000 description 1
- 230000001131 transforming effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
- F03B3/12—Blades; Blade-carrying rotors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
- F03B3/12—Blades; Blade-carrying rotors
- F03B3/121—Blades, their form or construction
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B17/00—Other machines or engines
- F03B17/06—Other machines or engines using liquid flow with predominantly kinetic energy conversion, e.g. of swinging-flap type, "run-of-river", "ultra-low head"
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03B—MACHINES OR ENGINES FOR LIQUIDS
- F03B3/00—Machines or engines of reaction type; Parts or details peculiar thereto
- F03B3/12—Blades; Blade-carrying rotors
- F03B3/125—Rotors for radial flow at high-pressure side and axial flow at low-pressure side, e.g. for Francis-type turbines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2250/00—Geometry
- F05B2250/70—Shape
- F05B2250/71—Shape curved
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
Description
Runner for Direct-connected Low-speed Small Mixed Flow Type Water Turbine Applied in
Hydrodynamic Energy-saving Cooling Tower
The invention relates to a cooling tower, in particular to a runner of a water turbine for driving the cooling tower, more specifically, the invention discloses a runner for a direct-connected low-speed small mixed flow type water turbine applied in a hydrodynamic energy-saving cooling tower, which is not provided with a speed reduction box and can enable the output rotational speed of the water turbine to be the rated value of the rotational speed of a fan through reasonable design of the runner of the water turbine so as to eliminate the speed reduction box used by a traditional reaction water turbine.
As we all know, in order to realize the energy-saving purpose, an existing air-conditioning cooling tower has started using a water turbine to drive a cooling fan, thereby fully utilizing energy of circulating water flow of the cooling tower to transform the energy to driving force of the water turbine; and the water turbine is used for transforming water energy to rotation mechanical energy for driving the cooling fan, thereby eliminating a traditional high-power cooling motor and realizing very significant energy-saving effect.
Presently, a circulating water abundant water head of the industrial air-conditioning cooling tower in China is 4m-15m, and the pressure water head of 0.5m-1m is required in the position for distributing water pipes, so that the water turbine for recovering the part of the circulating water abundant water head works in an environment with back pressure; but the rotational speed of the fan of the cooing tower is lower, in order to realize direct connection with the fan of the cooling tower, the low-speed mixed flow type water turbine must be selected; however,
in the current spectrum of the water turbines in China, the low-speed mixed flow type water turbine which can meet the working environment and be directly connected with the cooling fan is still absent, the driving mode of connecting the ordinary mixed flow type water turbine with the fan of the cooling tower through a speed reducer needs to be adopted, as the working conditions of a speed reduction box are poorer, not only the noise is great and the service life is short, but also the manufacturing cost is correspondingly improved. Therefore, the mixed flow type water turbine which can meet the low unit rotational speed under the working environment and be directly connected with the fan of the cooling tower is designed, thereby having great practical significance.
The invention aims at designing a runner for a direct-connected low-speed small mixed flow type water turbine applied in a hydrodynamic energy-saving cooling tower against the problems that an output shaft of the existing water turbine of the cooling tower can only drive fan blades through a speed reduction box, the noise is large, fault is easy to occur and the manufacturing cost is high, thereby laying a foundation for finally eliminating a gear speed reduction transmission mechanism.
The technical scheme of the invention is as follows:
A runner for a direct-connected low-speed small mixed flow type water turbine applied in a hydrodynamic energy-saving cooling tower comprises an upper crown 1, a lower ring 3 and curved surface blades 2 mounted between the upper crown 1 and the lower ring 3, wherein the water inlet edge 4 is arranged at one end of each curved surface blade 2, each water inlet edge 4 is the high pressure side of the runner and is also the radial inflow side of water flow, the water outlet edge 5 is arranged at the other end of each curved surface blade 2, and each water outlet edge is the low pressure side of the runner and is also the axial outflow side of the water flow; connection points between the water outlet edges 5 and the lower ring 2 are A, the connection points between the water outlet edges 5 and the upper crown are B, and the runner is characterized in that the ratio of the height h of the water inlet edge 4 of each blade 2 to the diameter D1 corresponding to the water inlet edge 4 is 0.18-0.22, the ratio of the overall height
H of the blades 2 to the diameter D1 is (0.35-0.42, the ratio of the diameter D2 corresponding to the intersection point A of each water outlet edge 4 and the lower ring 3 to the diameter D1 is 0.4-0.6, the ratio of the diameter D3 corresponding to the intersection point B of each water outlet edge 4 and the upper crown to the diameter D1 is 0.3-0.45, the ratio of the diameter D4 in the position of a water drain round platform on the upper crown 1 to the diameter D1 is 0.1-0.2, and the relationship between the diameter D1 and the rotational speed of cooling fan blades is
Dl=nl11x JH py. wherein nll is a constant number and called as unit rotational speed, the value range is 28-42, n is the rated rotational speed of the cooling fan blades, and H is the inlet water pressure (water column is taken as unit: m).
The number of the curved surface blades 2 is 16-20, and the ratio of the minimal thickness to the maximal thickness of wing shapes of the blades is 0.28-0.34.
The invention has the following benefits:
The invention can lay a foundation for finally eliminating the speed reduction box for the water turbine for the cooling tower, by utilizing the runner designed by the invention, the using requirements can be fully met, and experiments prove that the output rotational speed of the water turbine equipped with the runner can fully meet the using requirements, and the pulsation range of the rotational speed is smaller.
The structure is simple, and the mounting and the use are very convenient.
Against the characteristics of the water turbine for the cooling tower, the unit rotational speed nll is creatively reduced from the level of not less than 80 during actual application of the traditional reaction water turbine to 28-42; simultaneously, a curve equation of key elements, namely guide vanes, which can affect the efficiency of the water turbine, is determined according to the unit rotational speed, the relationship between the size of the runner and the size D1 of the water inlet edges of the blades is given out through a lot of calculation and experiments, and the relationship between the D1 and the rotational speed of a cooling fan is simultaneously given out, thereby providing a fast and convenient way for reasonably designing the runner.
Experiments prove that as long as the unit rotational speed is 28-42, the determined size D1 of the water inlet edges of the blades and the determined size of the runner can maintain the overall efficiency of the water turbine at about 86%, when the unit rotational speed is more than 42 or less than 28, the efficiency is in linear sharp decline.
Figure 1 is a schematic diagram of stereostructure of runner of the invention.
Figure 2 is a size schematic diagram of all parts of the runner of the invention.
Figure 3 is a schematic diagram of stereostructure of curved surface blade of the invention.
Figure 4 is a three-view projection drawing of curved surface blade of the invention.
In combination of the figures and the embodiment, the invention is further described as follows.
As shown in Figure 2, a runner for a direct-connected low-speed small mixed flow type water turbine applied in a hydrodynamic energy-saving cooling tower comprises an upper crown 1, a lower ring 3 and 16-20 curved surface blades 2 mounted between the upper crown 1 and the lower ring 3, as shown in Figure 1, the curved surface blades 2 are in wing-shaped structures, as shown in Figure 3 and Figure 4, the ratio of the minimal thickness to the maximal thickness of the wing shapes of the blades is 0.28-0.34, the water inlet edge 4 is arranged at one end of each curved surface blade 2, each water inlet edge 4 is the high pressure side of the runner and is also the radial inflow side of water flow, the water outlet edge 5 is arranged at the other end of each curved surface blade 2, and each water outlet edge is the low pressure side of the runner and is also the axial outflow side of the water flow; connection points between the water outlet edges and the lower ring 2 are A, the connection points between the water outlet edges 5 and the upper crown are B, the ratio of the minimal thickness to the maximal thickness of the wing shapes of the curved surface blades is 0.28-0.34, the relationship between the size of the curved surface blades 2 and the sizes of the related parts of the whole runner is as follows: the ratio of the height h of each water inlet edge 4 to the diameter D1 corresponding to the water inlet edge 4 is 0.18-0.22, the ratio of the overall height H of the blades 2 to the diameter D1 is 0.35-0.42, the ratio of the diameter D2 corresponding to the intersection point A of each water outlet edge 4 and the lower ring 3 to the diameter D1 is 0.4-0.6, the ratio of the diameter D3 corresponding to the intersection point B of each water outlet edge 4 and the upper crown to the diameter D1 is 0.3-0.45, and the ratio of the diameter D4 in the position of a water drain round platform on the upper crown 1 to the diameter D1 is 0.1-0.2, as shown in Figure 2. The relationship between the diameter D1 of each water inlet edge and the rotational speed of cooling fan blades is
Dl=nl11x JH /m, wherein n11 is a constant number and called as unit rotational speed, the value range is 28-42, n is the rated rotational speed of the cooling fan blades, and H is the inlet water pressure (water column is taken as unit: m).
When in specific implementation, once the rotational speed of the fan blades of the cooling tower is determined, the value of nll is further selected according to a using environment, generally speaking, the selected value in the South is higher, the selected value in the North is lower, under most of the situations, the appropriate selected value is 35, then the value of D1 can be determined by the inlet water pressure H, and the sizes of all the parts, namely the curved surface blades, the upper crown and the lower ring are finally determined according to the value of D1, thereby getting the runner meeting the requirement on the rated rotational speed.
Several specific calculation examples are described as follows:
Example 1
Assume that n11 is 35, the inlet water pressure H is 13m and the rated rotational speed n of fan blades is 1361r/min, then D1 is 0.928m, and one curved surface blade in the shape as shown in
Figures 3 and 4 is designed. The actually measured rotational speed of the mounted fan blades is 137r/min, which is in line with the design requirement.
Example 2
Assume that n11 is 30, the inlet water pressure H is 15m and the rated rotational speed n of fan blades is 140r/min, then D1 is 0.830m, and one curved surface blade in the shape as shown in
Figures 3 and 4 is designed. The actually measured rotational speed of the mounted fan blades is 138r/min, which is in line with the design requirement.
Example 3
Assume that n11 is 40, the inlet water pressure H is 15m and the rated rotational speed n of fan blades is 130r/min, then D1 is 1.192m, and one curved surface blade in the shape as shown in
Figures 3 and 4 is designed. The actually measured rotational speed of the mounted fan blades is 131r/min, which is in line with the design requirement.
Example 4
Assume that n11 is 28, the inlet water pressure H is 13m and the rated rotational speed n of fan blades is 1361r/min, then D1 is 0.742m, and one curved surface blade in the shape as shown in
Figures 3 and 4 is designed. The actually measured rotational speed of the mounted fan blades is 130r/min, which is in line with the design requirement.
Example 5
Assume that n11 is 42, the inlet water pressure H is 10m and the rated rotational speed n of fan blades is 140r/min, then D1 is 0.949m, and one curved surface blade in the shape as shown in
Figures 3 and 4 is designed. The actually measured rotational speed of the mounted fan blades is 145r/min, which is in line with the design requirement.
Example 6
Assume that n11 is 27, the inlet water pressure H is 13m and the rated rotational speed n of fan blades is 1361r/min, then D1 is 0.712m, and one curved surface blade in the shape as shown in
Figures 3 and 4 is designed. The actually measured rotational speed of the mounted fan blades is 110r/min, which is not in line with the design requirement.
Example 7
Assume that n11 is 43, the inlet water pressure H is 10m and the rated rotational speed n of fan blades is 140r/min, then D1 is 0.969m, and one curved surface blade in the shape as shown in
Figures 3 and 4 is designed. The actually measured rotational speed of the mounted fan blades is 120r/min, which is not in line with the design requirement.
For those skilled in the art, a wood former can be obtained very conveniently by referring to the relationship among all parameters between the blades and the runner, as well as the relationship between the diameter of the water inlet edge of each blade and the unit rotational speed, and between the water head and the rotational speed of the fan blades, and then an ideal conversion structure can be obtained by design after finishing the wood former directly or slightly.
The non-involved parts are the same with the prior art or can be realized by adopting the prior art. fy
Claims (2)
1. A runner for a direct-connected low-speed small mixed flow type water turbine applied in a hydrodynamic energy-saving cooling tower, comprising an upper crown (1), a lower ring (3) and curved surface blades (2) mounted between the upper crown (1) and the lower ring (3), wherein the water inlet edge (4) is arranged at one end of each curved surface blade (2), each water inlet edge (4) is the high pressure side of the runner and is also the radial inflow side of water flow, the water outlet edge (5) is arranged at the other end of each curved surface blade (2), and each water outlet edge is the low pressure side of the runner and is also the axial outflow side of the water flow; connection points between the water outlet edges (5) and the lower ring (3) are A, the connection points between the water outlet edges (5) and the upper crown are B, and the runner is characterized in that the ratio of the height h of the water inlet edge (4) of each blade (2) to the diameter D1 corresponding to the water inlet edge (4) is
0.18-0.22, the ratio of the overall height H of the blades (2) to the diameter D1 is 0.35-0.42, the ratio of the diameter D2 corresponding to the intersection point A of each water outlet edge (5) and the lower ring (3) to the diameter D1 is 0.4-0.6, the ratio of the diameter D3 corresponding to the intersection point B of each water outlet edge (5) and the upper crown to the diameter D1 is 0.3-0.45, the ratio of the diameter D4 in the position of a water drain round platform on the upper crown (1) to the diameter D1 is 0.1-0.2, and the relationship between the diameter D1 and the rotational speed of cooling fan blades is Dl=nllx~H /m, wherein D1 is the diameter corresponding to each water inlet edge (4), the unit of the diameter D1 is m, nll is a constant number and called as unit rotational speed, the value range is 28-42, n is the rated rotational speed of the cooling fan blades, the unit of the rated rotational speed n is r/min, H is the inlet water pressure, and the unit of water column is m water column.
2. The runner according to claim 1, characterized in that the number of the curved surface blades (2) is 16-20, and the ratio of the minimal thickness to the maximal thickness of wing shapes of the blades is 0.28-0.34.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009100273099A CN101560936B (en) | 2009-05-27 | 2009-05-27 | Runner used for direct connection low-speed small-scale mixed-flow turbine of hydrodynamic energy-saving cooling tower |
| PCT/CN2010/073241 WO2010135989A1 (en) | 2009-05-27 | 2010-05-25 | Rotating wheel used for direct-connection low-speed small-scale mixed-flow hydroturbine of hydrodynamic energy-saving cooling tower |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| SG176259A1 true SG176259A1 (en) | 2012-01-30 |
Family
ID=41219876
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| SG2011087624A SG176259A1 (en) | 2009-05-27 | 2010-05-25 | Rotating wheel used for direct-connection low-speed small-scale mixed-flow hydroturbine of hydrodynamic energy-saving cooling tower |
Country Status (14)
| Country | Link |
|---|---|
| US (1) | US9260969B2 (en) |
| EP (1) | EP2436916A4 (en) |
| JP (1) | JP2012528262A (en) |
| KR (1) | KR101327341B1 (en) |
| CN (1) | CN101560936B (en) |
| AU (1) | AU2010252464B2 (en) |
| BR (1) | BRPI1009075A2 (en) |
| CA (1) | CA2763303C (en) |
| MX (1) | MX2011012561A (en) |
| MY (1) | MY156030A (en) |
| RU (1) | RU2492351C1 (en) |
| SG (1) | SG176259A1 (en) |
| WO (1) | WO2010135989A1 (en) |
| ZA (1) | ZA201109424B (en) |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101560936B (en) | 2009-05-27 | 2010-12-08 | 南京星飞冷却设备有限公司 | Runner used for direct connection low-speed small-scale mixed-flow turbine of hydrodynamic energy-saving cooling tower |
| CN103953489B (en) * | 2013-08-02 | 2016-02-24 | 河海大学 | A kind of radial water turbine runner for directly driving blower fan of cooling tower |
| CN103485958B (en) * | 2013-10-12 | 2015-12-23 | 南京泉腾冷却设备有限公司 | A kind of Low-water-head turbine runner and application |
| CN103982362A (en) * | 2013-10-18 | 2014-08-13 | 河海大学 | Hydrodynamic direct-drive radial-flow water turbine of cooling tower |
| CN103982355A (en) * | 2013-10-18 | 2014-08-13 | 河海大学 | Radial flow water turbine rotating wheel for direct-drive cooling tower fan |
| ITRM20130580A1 (en) * | 2013-10-22 | 2015-04-23 | Gabriele Madonna | TURBINE WHICH IS CONSTANT ROTATION DIRECTLY CAUSED BY THE ALTERNATE MOVEMENTS OF THE FLOWS OF THE MARINE WAVES. |
| CN103743257B (en) * | 2014-01-09 | 2016-09-14 | 西华大学 | Efficient hydrodynamic cooling tower |
| CN104279115A (en) * | 2014-09-12 | 2015-01-14 | 乐山东方动力节能设备有限公司 | Novel special mixed flow type rotating wheel for hydraulic fan cooling tower driving |
| EP3276157A1 (en) * | 2016-07-25 | 2018-01-31 | GE Renewable Technologies | Hydraulic turbine |
| CN107725251A (en) * | 2017-10-10 | 2018-02-23 | 河海大学 | Reversible Pump-Turbine runner applied to low water head hydroenergy storage station |
| CN110516321B (en) * | 2019-08-06 | 2022-09-30 | 西安理工大学 | Method for calculating type selection of variable-speed water turbine rotating wheel |
| CN114576065B (en) * | 2022-03-03 | 2024-02-23 | 哈尔滨工业大学 | Water pump turbine runner with turn-around characteristic |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US963378A (en) * | 1905-09-23 | 1910-07-05 | Hans Lorenz | Turbine or centrifugal pump. |
| US3874819A (en) * | 1972-05-12 | 1975-04-01 | Hitachi Ltd | Francis type runner for pump turbine |
| JPS587830B2 (en) * | 1973-04-27 | 1983-02-12 | 株式会社日立製作所 | It's important to know what's going on in your life. |
| SE377829B (en) * | 1974-09-16 | 1975-07-28 | Karlstad Mekaniska Ab | |
| US4976319A (en) * | 1989-03-06 | 1990-12-11 | Hale Fire Pump Company | Water driven fan for firefighting |
| JP3357962B2 (en) * | 1993-08-26 | 2002-12-16 | 株式会社日立製作所 | Variable speed turbine power generator and variable speed turbine operating method |
| JP3898311B2 (en) * | 1997-11-26 | 2007-03-28 | 株式会社東芝 | Water wheel or pump water wheel |
| JP2003269313A (en) * | 2002-03-15 | 2003-09-25 | Mitsubishi Heavy Ind Ltd | Cavitation damage avoiding operating method of water wheel or pump water wheel, cavitation damage amount presuming method, and its program |
| JP2004108186A (en) | 2002-09-17 | 2004-04-08 | Mitsubishi Electric Corp | Cooling tower system of power generation plant |
| US7210904B2 (en) * | 2004-05-05 | 2007-05-01 | Bharat Heavy Electricals Ltd. | Runner blade for low specific speed Francis turbine |
| JP4751165B2 (en) * | 2005-10-12 | 2011-08-17 | 株式会社東芝 | Francis pump turbine |
| RU2321766C2 (en) * | 2006-05-19 | 2008-04-10 | Открытое акционерное общество "Силовые машины-ЗТЛ, ЛМЗ, Электросила, Энергомашэкспорт" (ОАО "Силовые машины") | Blade system for wheel of hydraulic turbine |
| JP4703578B2 (en) * | 2007-01-19 | 2011-06-15 | 東京電力株式会社 | Francis turbine |
| CN201071779Y (en) * | 2007-06-22 | 2008-06-11 | 金先培 | Pressure turbine for cooling tower |
| PL383367A1 (en) * | 2007-09-17 | 2009-03-30 | Sterplanet Inc. | Driving wheel of hydrous turbine |
| CN201133321Y (en) * | 2007-12-27 | 2008-10-15 | 东方电机股份有限公司 | Small runner crown exit port mixed flow turbine runner |
| CN101560936B (en) | 2009-05-27 | 2010-12-08 | 南京星飞冷却设备有限公司 | Runner used for direct connection low-speed small-scale mixed-flow turbine of hydrodynamic energy-saving cooling tower |
-
2009
- 2009-05-27 CN CN2009100273099A patent/CN101560936B/en not_active Expired - Fee Related
-
2010
- 2010-05-25 AU AU2010252464A patent/AU2010252464B2/en not_active Ceased
- 2010-05-25 US US13/322,553 patent/US9260969B2/en not_active Expired - Fee Related
- 2010-05-25 SG SG2011087624A patent/SG176259A1/en unknown
- 2010-05-25 KR KR1020117031152A patent/KR101327341B1/en not_active IP Right Cessation
- 2010-05-25 CA CA2763303A patent/CA2763303C/en not_active Expired - Fee Related
- 2010-05-25 BR BRPI1009075A patent/BRPI1009075A2/en not_active IP Right Cessation
- 2010-05-25 MY MYPI2011005750A patent/MY156030A/en unknown
- 2010-05-25 WO PCT/CN2010/073241 patent/WO2010135989A1/en active Application Filing
- 2010-05-25 EP EP10780070.8A patent/EP2436916A4/en not_active Withdrawn
- 2010-05-25 JP JP2012512190A patent/JP2012528262A/en active Pending
- 2010-05-25 RU RU2011152630/06A patent/RU2492351C1/en not_active IP Right Cessation
- 2010-05-25 MX MX2011012561A patent/MX2011012561A/en not_active Application Discontinuation
-
2011
- 2011-12-21 ZA ZA2011/09424A patent/ZA201109424B/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| RU2492351C1 (en) | 2013-09-10 |
| AU2010252464B2 (en) | 2013-10-31 |
| CA2763303C (en) | 2014-01-07 |
| JP2012528262A (en) | 2012-11-12 |
| CN101560936B (en) | 2010-12-08 |
| AU2010252464A1 (en) | 2012-02-02 |
| MX2011012561A (en) | 2012-04-30 |
| ZA201109424B (en) | 2012-12-27 |
| CA2763303A1 (en) | 2010-12-02 |
| RU2011152630A (en) | 2013-07-10 |
| KR101327341B1 (en) | 2013-11-11 |
| BRPI1009075A2 (en) | 2016-07-05 |
| KR20120033315A (en) | 2012-04-06 |
| US20130121838A1 (en) | 2013-05-16 |
| CN101560936A (en) | 2009-10-21 |
| EP2436916A1 (en) | 2012-04-04 |
| US9260969B2 (en) | 2016-02-16 |
| EP2436916A4 (en) | 2013-05-01 |
| MY156030A (en) | 2015-12-31 |
| WO2010135989A1 (en) | 2010-12-02 |
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